DE102020207056A1 - Vane compressor arrangement and pneumatic adjustment device with such an arrangement - Google Patents

Abstract

A vane compressor arrangement (10) for compressing a fluid for a pneumatic adjusting device (12) of a vehicle seat (14) is disclosed. The vane compressor arrangement (10) comprises a vane compressor (22) with a hollow cylindrical housing (24), a rotor element (26) arranged in the housing (24) and having a plurality of radially movable vane elements (30), two adjacent vane elements (30) in each case. define a respective compression chamber (36, 36 A, 36 B) of the vane compressor (22), a suction area (40) with a suction opening (42) for sucking in the fluid and a discharge area (44) with a discharge opening (46) for discharging the compressed Fluids. The vane compressor arrangement (12) further comprises a damping chamber (48) which is fluidly connected to the discharge area (44) and is designed to dampen pressure pulsations during the discharge of the compressed fluid, as well as a check valve (50) arranged in the damping chamber (48). which has an open position in which the discharge opening (46) is open, and a closed position in which the discharge opening (46) is closed, the check valve (50) being in the open position when the vane compressor (22) is in operation when the delivery area (44) is fluidly connected to a single compression chamber (36 A), and the check valve is in the closed position when the delivery area is fluidly connected to at least two compression chambers (36 A, 36 B).

Description

The present invention relates to a vane compressor arrangement, in particular for compressing a fluid for a pneumatic adjustment device of a vehicle seat. The present invention also relates to a pneumatic adjusting device with such a vane compressor arrangement.

In modern vehicle seats there are fluid chambers or fluid bubbles that can be filled with a pressure medium, in particular with a gaseous pressure medium such as compressed air, as adjusting elements in the area of the seat surface or seat back (together also referred to as seat contact surface). Such fluid chambers can be supplied with the pressure medium via a respective pressure medium line. By filling or emptying a respective fluid chamber with pressure medium, its volume is increased or decreased so that the properties of the seat contact surface, in particular its contour, can be changed. To fill the respective fluid chamber with pressure medium, the pressure medium is generated, for example, by a compressor or a compressor unit and is guided to a respective fluid chamber in a controlled manner via a suitable valve.

Different types of compressors are used to generate the pressure medium, for example rolling diaphragm compressors or vane compressors. In the case of the latter in particular, however, it has been shown that when the fluid is expelled in a pulsating manner on the pressure side of the vane compressor, undesired noises can arise due to the resulting pressure pulsations. Typical pulsation frequencies are in the range from 100 Hz to 3000 Hz, which are easily audible to the human ear and can therefore, for example, be perceived as annoying when adjusting the seat contact surface.

The object of the present invention is therefore to provide a vane compressor arrangement which reduces undesired noise as much as possible, in particular during operation of the vane compressor. Furthermore, it is the object of the present invention to provide a pneumatic adjusting device for a vehicle seat which has such a vane compressor arrangement.

These objects are achieved by a vane compressor arrangement according to claim 1 and a pneumatic adjustment device according to claim 10. Advantageous refinements are the subject of the subclaims.

According to a first aspect of the present invention, a vane compressor arrangement for compressing a fluid for a pneumatic adjustment device of a vehicle seat is provided. The vane compressor arrangement comprises a vane compressor with a hollow cylindrical housing and a rotor element arranged in the hollow cylindrical housing, the rotor element having a plurality of radially movable vane elements and two adjacent vane elements at least partially defining a respective compressor chamber of the vane compressor. The vane compressor further comprises a suction area with a suction opening for sucking in fluid, and a discharge area with a discharge opening for discharging compressed fluid. The vane compressor arrangement further comprises a damping chamber which is fluidly connected to the discharge area and is designed to dampen pressure pulsations during the discharge of the compressed fluid, as well as a check valve arranged in the damping chamber that has an open position in which the discharge opening is opened, so that the damping chamber and the dispensing area are fluidly connected to one another and have a closed position in which the dispensing opening is closed so that the damping chamber and the dispensing area are fluidly separated from one another. In an operation of the vane compressor, d. H. When the rotor element rotates and the associated movement of the vane elements, the check valve has the open position when the delivery area is fluidly connected to a single compression chamber, and the check valve is in the closed position when the delivery area of the vane compressor with at least two compression chambers is fluid connected is.

Since the check valve has the open position when the delivery area is fluidly connected to a single compression chamber and the closed position when the delivery area is fluidly connected to at least two compression chambers, the check valve can effectively and reliably dampen the pressure pulsations that arise in the delivery area when the compressed fluid is dispensed. The check valve is characterized by particularly high dynamics, since the check valve almost always changes between the open and the closed position when there is also a change between the fluid connection of the delivery area with a single and at least two compressor chambers. If, for example, only a single compression chamber is fluidly connected to the delivery area of the vane compressor, then the pressure in the delivery area usually rises to a nominal pressure value of the vane compressor. This leads to the non-return valve being pressed into the open position and thereby a fluid connection is established between the delivery area and the damping chamber. However, if, for example, when the rotor element continues to rotate, more than just one, i.e. at least two, compressor chambers are fluidly connected to the delivery area, the pressure in the delivery area is reduced below the aforementioned nominal pressure value of the vane compressor. This leads to the non-return valve changing from the open position to the closed position (for example due to the restoring force applied by the non-return valve), as a result of which the delivery area and the damping chamber are fluidly separated from one another. In other words, a change in position or circuit of the check valve takes place essentially synchronously with a change in the one or at least two compressor chambers that are fluidly connected to the delivery area. This fast and synchronized change of position or switching leads to effective damping of the pressure pulsations directly at the delivery area of the vane compressor. As a result, noise in the vane compressor arrangement is effectively and reliably reduced already at the level of the pressure pulsations that arise.

It when the check valve has a spring steel element is particularly advantageous. Spring steel is characterized by particularly good temperature resistance, in particular in a temperature range that is typically found in the almost isotropic compression of the fluid in the vane compressor. In addition, spring steel has a low mass with high spring stiffness, which results in an extremely short response time or response time to changing external pressure conditions. Spring steel therefore enables a dynamic change between the open and closed position of the check valve, which results in a high level of dynamics in the check valve. It is precisely these high dynamics that are necessary so that the check valve can effectively and reliably dampen the pressure pulsations that arise in the delivery area. The check valve can be designed entirely as a spring steel element. The check valve can, however, also have only one return element designed as a spring steel element, for example in the form of a spring or the like, which in turn interacts with a sealing tab or sealing element of the check valve, which can be made of rubber or the like, for example.

It is particularly advantageous if the check valve has a position change time of up to 10 ms, preferably up to 2 ms, within which the check valve is or can change between the open and the closed position. If the change between the open and the closed position, i.e. the change from the open position to the closed position, as well as the change from the closed position to the open position, takes place within a maximum of 10 ms, preferably a maximum of 2 ms that of a position change frequency of the check valve of a maximum of 1 / (2 * 10 ms) = 50 Hz, preferably a maximum of 1 / (2 * 2 ms) = 250 Hz, since the check valve for a change from the closed (or open) position to the next in the closed (or open) position (frequency = 1 / period) twice the duration of the position change, i.e. a maximum of 2 * 10 ms, preferably a maximum of 2 * 2 ms.

This means that with a compression chamber change frequency at the discharge area of up to 50 Hz, preferably up to 250 Hz, the pressure pulsation that occurs during the discharge of the compressed fluid can be effectively dampened with the position change time of the check valve of a maximum of 10 ms, preferably a maximum of 2 ms. Since the compressor chamber alternation frequency corresponds to the speed of the rotor element multiplied by the number of compressor chambers, a vane compressor with typically 8 compressor chambers can be operated in a low speed range of approximately up to 6 Hz, preferably approximately up to 33 Hz, without it becoming noticeable Noise is generated due to insufficient damping of the pressure pulsation. The number of compression chambers in vane compressors is typically in the range from 4 to 8, but can also have other values.

In a further preferred embodiment of the vane compressor arrangement according to the invention, the vane compressor arrangement also has a pressure accumulator which is fluidly connected to an outlet of the damping chamber, as well as a second check valve which is arranged in the pressure accumulator and which has a first position in which the outlet of the damping chamber is open, so that the damping chamber and the pressure accumulator are fluidly connected to one another and have a second position in which the outlet of the damping chamber is closed so that the pressure accumulator and the damping chamber are fluidly separated from one another. By providing a second, separate check valve in the pressure accumulator of the vane compressor arrangement, it is possible to provide two check valves with different responses. This enables greater flexibility when designing the check valves. For example, the first check valve in the damping chamber can be designed with regard to the dynamics already mentioned, while the second check valve in the pressure accumulator can be designed with regard to a desired sealing performance or tightness.

In a particularly preferred embodiment, the second check valve is designed to have the first position both in the open position and in the closed position of the first check valve. As a result, the second check valve has far fewer switching cycles than the first check valve, which switches with each change between one and at least two valve chambers. The second check valve is therefore exposed to significantly lower material stress compared to the first check valve, which leads to a longer service life and better long-term stability of the second check valve.

In a further preferred embodiment, the second check valve has the second position, ie the position in which the outlet of the damping chamber is closed, only when a delivery pressure of the vane compressor falls below a pressure in the pressure accumulator. The second check valve can in particular be designed in such a way that it closes in particular when the delivery pressure drops below the pressure of the pressure accumulator. As a result, a particularly good tightness can be achieved at the outlet of the damping chamber, which prevents fluid from escaping from the pressure accumulator reliably and over a long operating period of the vane compressor.

In a further preferred embodiment, the second check valve also has a position change time of 20 ms or more, in which the second check is or can change between the first position and the second position. This position change time of at least 20 ms, which is comparatively large in comparison to the first check valve, leads to a comparatively low dynamic of the second check valve. However, the lower dynamic of the second check valve results in an improved sealing effect at the outlet of the damping chamber.

It is particularly advantageous if the second check valve is made of an elastic material such as silicone or rubber. Elastic materials are characterized by a particularly good tightness property. Elastic materials are less reactive than spring steel, for example. However, the short response time and high dynamics of the second check valve are not required at all.

In a further embodiment of the vane compressor arrangement according to the invention, the arrangement also has a controllable valve which is fluidly connected to a pressure accumulator outlet of the pressure accumulator and is designed to controllably supply fluid present in the pressure accumulator to a consumer. This enables, for example, a controlled supply of the compressed fluid, for example to a fluid bladder of a pneumatic adjustment device of a vehicle seat.

According to a second aspect of the invention, a pneumatic adjustment device for adjusting a contour of a seat contact surface of a vehicle seat is provided. The pneumatic adjustment device has a fluid bladder for adjusting the contour of the seat contact surface and a vane compressor arrangement according to the first aspect or its configurations, the fluid bladder being fluidly connected to the controllable valve of the vane compressor arrangement.

• 1 eine schematische Ansicht einer Ausführungsform einer erfindungsgemäßen Flügelzellenverdichteranordnung, wobei ein Abgabebereich eines Flügelzellenverdichters der Flügelzellenverdichteranordnung fluidmäßig mit lediglich einer einzigen Ventilkammer des Flügelzellenverdichters verbunden ist, und
• 2 eine schematische Ansicht der Ausführungsform von 1, wobei der Abgabebereich in der Ansicht von 2 fluidmäßig mit zwei Ventilkammern des Flügelzellenverdichters verbunden ist,

Other features and objects of the present invention will become apparent to those skilled in the art after practicing the present teachings and reviewing the accompanying drawings. Show it:

• 1 a schematic view of an embodiment of a vane compressor arrangement according to the invention, wherein a delivery area of a vane compressor of the vane compressor arrangement is fluidly connected to only a single valve chamber of the vane compressor, and
• 2 FIG. 3 is a schematic view of the embodiment of FIG 1 , the delivery area in the view of 2 is fluidly connected to two valve chambers of the vane compressor,

Elements of the same construction or function are provided with the same reference symbols in all the figures.

Let it be up first 1 referenced, which is a schematic view of a vane compressor assembly 10 indicates. In the specific example of 1 becomes the vane compressor assembly 10 in a pneumatic adjustment device 12th a vehicle seat 14th used. The pneumatic adjustment device 12th is used to adjust a contour 16 a seating area 18th of the vehicle seat 14th . The vehicle seat 14th has for this purpose a fluid bladder that can be filled with fluid 20th on. By filling and emptying the fluid bladder 20th with fluid, its volume changes, creating the contour 16 the seating area 18th is adjustable.

As in 1 can be seen, is the vane compressor arrangement 10 fluidly with the fluid bladder 20th connected and is used in particular to fill the fluid bladder 20th with fluid. The vane compressor assembly 10 has a vane compressor for this purpose 22nd on. The vane compressor 22nd has a hollow cylindrical housing 24 on, in the inside of which is a rotor element 26th is arranged. The rotor element 26th is around an axis 28 rotatable and has several radially movable wing elements or slides 30th on. By turning the rotor element 26th and thus on the wing elements 30th acting centrifugal forces are the wing elements 30th against an inside wall 32 of the hollow cylindrical housing 24 pressed. Two adjacent wing elements each 30th define together with the inner wall 32 of the hollow cylindrical housing 24 and an outer wall 34 of the rotor element 26th (together with the top and bottom surface of the housing 24 ) a respective compression chamber 36 of the vane compressor 22nd as is well known to those skilled in the art for such compressors. Two adjacent compression chambers are designated by 36 A and 36 B as an example.

The vane compressor 22nd also has a suction area 40 with a suction port 42 for sucking in fluid. That in the intake area 40 sucked fluid is then in operation of the vane compressor 22nd , that is, when rotating the rotor element 26th , into the respective compression chamber 36 sucked in. When rotating the rotor element 26th that will be in the compression chamber 36 the fluid located is then increasingly compressed in a manner known to the person skilled in the art, before the compressed fluid is finally in a delivery area 44 of the vane compressor 22nd via a dispensing opening 46 is delivered.

As also in 1 can be seen is the vane compressor 22nd and especially the delivery area 44 of the vane compressor 22nd fluidly with a damping chamber 48 the vane compressor assembly 10 connected. The damping chamber 48 serves to dampen pressure pulsations that occur when the compressed fluid is released.

Inside the damping chamber 48 is a first check valve 50 arranged. The first check valve 50 is movable between an open position and a closed position. 1 shows the check valve 50 in an open position and 2 shows the check valve 50 in a closed position.

In the open position, the check valve opens 50 the dispensing opening 46 or in an open position of the check valve 50 is the delivery opening 46 open. This creates the damping chamber 48 and the delivery area 44 fluidly connected to each other.

In the in 2 shown closed position of the check valve 50 closes the check valve 50 the dispensing opening 46 or is the delivery opening 46 closed. This creates the damping chamber 48 and the delivery area 44 fluidly separated from each other.

The check valve 50 is now designed such that in one operation of the vane compressor 22nd , that is, when rotating the rotor element 26th , the check valve 50 then has the open position when the delivery area with a single compression chamber 36 , for example. The compression chamber 36 A of 1 , is fluidly connected. If the delivery area 44 is fluidly connected to only a single compression chamber 36 A, then the pressure in the delivery area rises 44 up to a nominal pressure value so that the compressed fluid passes the check valve 50 can push into the open position. In this case, the check valve opens 50 the dispensing opening 46 so that in the delivery area 44 existing compressed fluid in the damping chamber 48 can flow.

Let it be up now 2 referenced in which the fluid compressor assembly 10 from 1 as well as the pneumatic adjustment device 12th from 1 are shown.

In 2 has the rotor element 26th - compared to the position of the rotor element 26th in 1 - moved a certain amount in a clockwise direction. Due to the movement of the rotor element 26th which inevitably in the operation of the rotor element 26th is the delivery area 44 now no longer only with a single compression chamber 36 A (cf. 1 ) but with two compressor chambers 36 A and 36 B fluidly connected.

By the delivery area 44 is now fluidly connected to two compressor chambers 36 A, 36 B, the amount in the delivery area is reduced 44 existing pressure under those related to 1 described nominal pressure value. This has the consequence that it affects the check valve 50 acting compressive force that is still in 1 to open the check valve 50 has decreased. As a result of the check valve 50 acting, reduced pressure force in the delivery area 44 changes the check valve 50 from the in 1 open position shown in 2 shown, closed position. This has the consequence that now the damping chamber 48 and the delivery area 44 are fluidly separated from each other. The fluid separation of the damping chamber 48 and delivery area 44 leads to the fact that due to the change of a single valve chamber 36 A, the one with the delivery area 44 is fluidly connected to at least two valve chambers 36 A, 36 B, which are connected to the delivery area 44 are fluidly connected, resulting pressure pulsation does not enter the damping chamber 48 is propagated and also no backflow of fluid from the damping chamber 48 in the delivery area 44 and thus in the vane compressor 22nd he follows. This creates noise due to pressure pulsations in the delivery area 44 arises, effectively and reliably reduced.

The check valve 50 is designed in such a way that there is a comparatively short position change time within which the check valve 50 can switch between the open and the closed position. The position change time of the check valve 50 is a maximum of 10 ms, preferably a maximum of 2 ms. A position change time of 10 ms or 2 ms corresponds to a position change frequency of the check valve of a maximum of 1 / (2 * 10 ms) = 50 Hz or a maximum of 1 / (2 * 2 ms) = 250 Hz, since the check valve 50 for a change from the closed (or open) position to the next closed (or open) position (frequency = 1 / period) twice the position change time, i.e. 2 * 10 ms or 2 * 2 ms is required. That means with a compression chamber change frequency at the delivery area 44 of up to 50 Hz or up to 250 Hz, with the position change time of the check valve 50 of a maximum of 10 ms or a maximum of 2 ms, the pressure pulsation that occurs when the compressed fluid is released can be effectively damped. In other words, the check valve 50 virtually with every change from one compression chamber 36 A to two compression chambers 36 A, 36 B at the delivery area 44 perform a position change from an open to a closed position.

In addition, since the compressor chamber alternation frequency of the speed of the rotor element 26th multiplied by the number of compression chambers 36 the vane compressor can 22nd , which in the specific example of 1 and 2 eight compression chambers 36 has, be operated in a low speed range of approximately up to 6 Hz, preferably approximately up to 33 Hz, without there being any noticeable noise due to insufficient damping of the pressure pulsation. In other examples, not shown, the number of compression chambers 36 of the vane compressor 22nd naturally also have other values.

Furthermore, in the specific example of 1 the check valve 50 designed as a spring steel element. Spring steel not only has a high temperature resistance in the temperature range that is typically found in the almost isotropic compression of the fluid in the vane compressor 22nd is present. Spring steel also has a low mass with a high spring stiffness, which leads to a short reaction time or a short response time and thus a high dynamic for the check valve 50 leads. In other embodiments, not shown, the check valve 50 naturally have a resetting element designed as a spring steel element, which in turn interacts with a sealing element of the check valve, which is formed for example from an elastic material such as rubber or the like, and provides the resetting force required for the check valve with the correspondingly high dynamics.

It is now up again 1 referenced.

As in 1 shown comprises the vane compressor assembly 10 also a pressure accumulator 52 on. The pressure accumulator 52 is with an outlet 54 the damping chamber 48 fluidly connected. In the damping chamber 52 is a further or second check valve 56 arranged. This second check valve 56 is movable between a first position and a second position. In the first position of the check valve 56 that are in both 1 as well as in 2 shown is the outlet 54 opened so that the accumulator 52 and the damping chamber 48 are fluidly connected to one another. In the second position of the second check valve 56 however, is the outlet 54 the damping chamber 48 closed so that the pressure accumulator 52 and the damping chamber 48 are fluidly separated from each other.

How by comparing 1 With 2 can be seen, has the second check valve 56 the first position both in the open position of the first check valve 50 (compare 1 ) as well as in the closed position of the first check valve 50 (compare 2 ) on. The second check valve 56 thus has far fewer switching cycles than the first check valve 50 on. The second check valve 50 is designed such that it has a position change time of at least 20 ms in which the second check valve 56 can switch between the first position and the second position. True is the second check valve 56 compared to the first check valve 50 less dynamic. However, this is also not necessary because the pressure pulsations are already exerted by the first dynamic check valve 50 effectively dampened. The second check valve 56 is made of an elastic material such as silicone or rubber. The elastic material admittedly has a longer reaction time or a longer duration of the change of position than that in connection with the first check valve 50 mentioned spring steel. However, the elastic material has a particularly good tightness property compared to spring steel. This property can be used for the outlet 54 the damping chamber 48 to close reliably and fluid-tight. The second check valve 56 is designed such that the second check valve 56 the second position, i.e. the position in which the second check valve 56 the outlet 54 closes, only when a delivery pressure of the vane compressor 22nd under a pressure in the accumulator 52 sinks. This allows the pressure accumulator 52 for example when the vane compressor is shut down 22nd effectively kept pressure-tight.

Although in 1 and 2 the pressure accumulator 52 and the damping chamber 48 are shown comparatively the same size, has the damping chamber 48 a volume that is in a range from approximately 10 times to approximately 1000 times the volume of the pressure accumulator 52 located.

As also in 1 shown comprises the vane compressor assembly 10 also a controllable valve 58 on, the one with an accumulator outlet 60 of the accumulator 52 fluidly connected. The controllable valve 58 enables the controlled supply of the in the pressure accumulator 52 located, compressed fluids to a consumer, such as in 1 and 2 illustrated fluid bladder 20th .

Although the vane compressor assembly 10 is described in connection with a pneumatic adjustment device for the pneumatic adjustment of a contour of a seat system of a vehicle seat, it is of course also possible that the vane compressor arrangement 10 can be used for other applications that require a quiet supply of compressed fluid.

Claims (10)

Vane compressor arrangement (10) for compressing a fluid for a pneumatic adjusting device (12) of a vehicle seat (14), with: - A vane compressor (22) with - a hollow cylindrical housing (24), - A rotor element (26) which is arranged in the housing (24) and has a plurality of radially movable vane elements (30), two adjacent vane elements (30) defining a respective compressor chamber (36, 36 A, 36 B) of the vane compressor (22) , - A suction area (40) with a suction opening (42) for sucking in the fluid - A dispensing area (44) with a dispensing opening (46) for dispensing the compressed fluid, - A damping chamber (48) which is fluidly connected to the delivery area (44) and is designed to dampen pressure pulsations during the delivery of the compressed fluid, and - A check valve (50) which is arranged in the damping chamber (48) and has an open position in which the discharge opening (46) is open so that the damping chamber (48) and the discharge area (44) are fluidly connected, and a closed position in which the dispensing opening (46) is closed, so that the damping chamber (48) and the dispensing area (44) are fluidly separated from one another, the check valve (50) having the open position when the vane compressor (22) is in operation, when the discharge area (44) is fluidly connected to a single compression chamber (36 A), and the check valve is in the closed position when the discharge area is fluidly connected to at least two compression chambers (36 A, 36 B). Vane compressor arrangement (10) according to Claim 1 wherein the check valve (50) comprises a spring steel member. Vane compressor arrangement (10) according to Claim 1 or 2 wherein the check valve (50) has a position change time of up to 10 ms, preferably up to 2 ms, within which the check valve (50) can be changed between the open and the closed position. Vane compressor arrangement (10) according to one of the preceding claims, further comprising: - A pressure accumulator (52) which is fluidly connected to an outlet (54) of the damping chamber (48), and - A second check valve (56) arranged in the pressure accumulator (52), which has a first position in which the outlet (54) of the damping chamber (48) is open, so that the pressure accumulator (52) and the damping chamber (48) are fluidly connected , and a second position in which the outlet (54) of the damping chamber (48) is closed so that the pressure accumulator (52) and the damping chamber (48) are fluidly separated from one another. Vane compressor arrangement (10) according to Claim 4 wherein the second check valve (56) is designed to have the first position both in the open position and in the closed position of the first check valve (50). Vane compressor arrangement (10) according to Claim 4 or 5 , wherein the second check valve (56) has the second position only when a delivery pressure of the vane compressor (22) falls below a pressure in the pressure accumulator (52). Vane compressor arrangement (10) according to one of the Claims 4 until 6th , wherein the second check valve (52) has a position change time of 20 ms or more, in which the second check valve (52) can be changed between the first position and the second position. Vane compressor arrangement (10) according to one of the Claims 4 until 7th , wherein the second check valve (56) is formed from an elastic material. Vane compressor arrangement (10) according to one of the Claims 4 until 8th , further comprising: - a controllable valve (58) which is fluidly connected to a pressure accumulator outlet (60) of the pressure accumulator (52) and is designed to controllably supply fluid present in the pressure accumulator (52) to a consumer. Pneumatic adjusting device (12) for adjusting a contour (16) of a seat contact surface (18) of a vehicle seat (14), with: - a fluid bladder (20) for adjusting the contour (16) of the seat contact surface (18) and - a vane compressor arrangement (10) after Claim 9 wherein the fluid bladder (20) is fluidly connected to the controllable valve (58) of the vane compressor arrangement (10).

Images